Bearing for a dynamometer with a vibration unit and its use in upper and lower limb vibration dynamometers

Abstract

A bicycle ergometer is disclosed, comprising at least one pedal mechanism for a user and a vibration unit, characterized in that the bearing (29) of the pedal mechanism is mounted pivotable about a horizontal rotation axis (45).

Description

Technical Field

[0001] This invention relates to a force gauge having a vibration unit, a method for operating such a force gauge, a method for manufacturing such a force gauge, and applications of such a force gauge. Background Technology

[0002] In order to positively and effectively influence the individual performance structure of rehabilitation / elderly patients or competitive athletes, it is necessary to translate as many quantitative external training stimuli as possible into different structural levels of the human body in a balanced and adaptive manner. In this process, both conditional components (strength, endurance, speed, flexibility) and coordination (neuromotor) components should be considered within the scope of the training equipment used.

[0003] By optimizing physiological performance through reactivating pathologically degenerated functional systems in the human body or enhancing the ability of non-destructive functional systems, the diversity of vibration training equipment offers new training options. Although medical vibration training (MVT) has begun commercial applications, the scientific validation of this method is still in the basic research stage.

[0004] Devices that transmit vibrational energy to users are known from multiple public disclosures:

[0005] In this way, US 4,570,927 discloses a device in which, for example, a crank unit moves and vibrates the leg of a paraplegic patient, the crank unit being driven by a motor.

[0006] NL 102 16 19C describes a device in which vibrational energy is transmitted to the upper limbs via a handle.

[0007] According to a device of DE 102 41 340A1, a vibrator selectively transmits vibrations to expanded muscle structures.

[0008] DE 102 25 323B4 provides protection for another type of vibrating device in which random resonances are transmitted to the user through a complex mechanical structure.

[0009] DE 196 39 477A1 illustrates a device having a seat, handles, and a vibration unit, through which the user's feet are subjected to vibrational impact.

[0010] The five devices mentioned above do not disclose, for example, how they are combined with a force gauge via a braking unit connected to the crankshaft, or how they are used as a force gauge, and most of them also do not disclose details about how the vibration is generated.

[0011] According to DE 103 13 524B3, a training device in which one or more contact points with the person being trained, which are susceptible to vibrational shock, are vibrationally isolated by one or more damping elements, such that all modules used to support the user's body parts are set in vibration.

[0012] A vibration dynamometer is known from WO 2006 / 69988A1, in which a base frame bearing is fixedly connected to a vibrating plate, which is vibrated by two counter-rotating vibration motors. Its disadvantage is the generation of non-directional vibration, the amplitude of which decreases depending on the mechanical load on the pedal crank or the adjustment of the dynamometer brake. The connection between the pedal crank and the dynamometer brake can only be achieved via a bicycle chain with a chain tensioner to compensate for the differences in length and position between the base frame bearing and the dynamometer. This results in unpleasant noise and requires additional securing measures to prevent the chain from jumping off the front sprocket.

[0013] EP 2 158 944 A2 describes a vibration force gauge with variable amplitude. It does not disclose how the vibration is specifically generated or how this change in amplitude is achieved.

[0014] WO-A-2010110670 describes a stationary training and exercise device for simulating the driving of bicycles, motorcycles, amphibious vehicles, airplanes, and similar human-powered vehicles, wherein the basic structure includes a first frame supported on the floor and a second frame support leg connected to the first frame on an axle, the second frame being rotatably tiltable relative to the first frame, and wherein the tilt can be controlled using handlebars or a steering wheel via a connection between a steering column and a reference to the first frame.

[0015] EP-A-2008695 relates to a training device comprising a mechanism that is rotated by a user of the training device via a drive mechanism that rotates about an axis of rotation; and a vibration device that causes the drive mechanism to vibrate, wherein the vibration device includes an electric motor that rotates about the axis of rotation, the electric motor having at least one weight that rotates the electric motor about the axis of rotation, wherein the weight is eccentrically positioned relative to the axis of rotation. The electric motor is freely pivotable about a fulcrum pin that extends parallel to the axis of rotation of the electric motor, wherein the fulcrum pin is positioned above the electric motor below the axis of rotation of the drive mechanism, and the electric motor is pivotally connected to a support that supports the axis of rotation of the drive mechanism, wherein the support is connected to the frame of the exercise equipment via a spring mechanism.

[0016] US-A-2014024502 ​​describes a training bicycle with a base support and an upright support structure. The seat, handlebar assembly, pedal assembly, and resistance assembly are connected to the upright support structure. The upright support structure is pivotally connected to the base support, allowing it to move between different tilt positions. One or more vibration components can be connected to the bicycle in different positions to vibrate desired parts of the bicycle, such as the handlebar assembly, seat, or pedal assembly. Vibrations are transmitted to the user during exercise to provide different physiological benefits.

[0017] CN-A-106618946 discloses a rehabilitation training bed for lower limb training. The rehabilitation training bed includes a bed frame, a lower limb training system mounted on the bed frame and movable horizontally relative to the bed frame, and includes a lower limb trainer and a lower limb trainer position adjustment mechanism. The lower limb trainer position adjustment mechanism is assembled on the bed frame, and the lower limb trainer is fixedly connected to the end of the lower limb trainer position adjustment mechanism. According to the accompanying drawings, this design can solve the problems of existing rehabilitation beds having limited training modes, large size, and large space occupation.

[0018] KR-A-20180100781 relates to a virtual reality-linked intelligent riding simulator, which allows users to experience virtual reality while moving in the same way as actually riding a bicycle, motorcycle, vehicle, etc. in a virtual space. The virtual reality-linked intelligent riding simulator includes: a frame unit for providing a riding space for the user; a tilting plate for supporting the frame unit, which rotates forward and backward; a front / rear slope realization unit for rotating the frame unit relative to the tilting plate unit in the front-rear direction according to signals related to the front and rear slopes of the road surface in the virtual riding space, input from the outside; a base plate unit for supporting the left and right rotation of the tilting plate unit; and a left / right tilt realization unit for supporting the left and right bottom areas of the tilting plate unit via a drive shaft and multiple cams, the drive shaft being supported to rotate horizontally on the base plate unit, and the multiple cams being integrally coupled to and rotating with the drive shaft. The tilting plate unit is driven to tilt left and right according to signals related to the left and right slopes of the road surface in the virtual riding space, input from the outside. Therefore, by realizing various riding environments and postures similar to those of an actual user riding, a realistic feeling of actual riding in a virtual riding space can be provided. Summary of the Invention

[0019] All the aforementioned force gauge systems are based on the principle of using training devices on a vibration plate to position the user. All components supporting the trainee apply vibrational energy to the body parts or corresponding body areas in contact with those components. This results in whole-body vibration (WBV) exceeding the critical occupational health value according to DIN ISO 2631 to some extent. Resonance conflict reduces the duration of application, leading to minimized efficiency (due to time constraints). The characteristics of MVT devices—isolation from uniform neuromotor stimulation for intramuscular coordination, while focusing on the conditioned intensity component—result in a deficiency in WBV's versatility in broad conditioned coordination. Existing MVT products only cover selective aspects of training therapy; these devices fail to realize the holistic training concept. They must be combined with conservative training equipment (e.g., combined with cardiac equipment during warm-up / cool-down phases, or supplemented with mechanical resistance training).

[0020] The object of this invention is to provide a mounting for a force gauge with a vibration unit, which thus provides an optimal mounting for the base bearing of the vibration, wherein the amplitude and frequency of the vibration are adjustable because the vibration acts essentially only in one direction, preferably vertically, the amplitude is substantially independent of the load on the vibration unit, and a vibration frequency of up to 50 Hz (Hertz) will be achieved. Another object of this invention is the use of the mounting according to the invention in vibration force gauges for the lower and upper limbs.

[0021] The present invention accordingly relates to a force gauge, particularly a bicycle force gauge, having at least one pedal device for a user and having the vibration unit as described in claim 1.

[0022] This invention primarily relates to a bicycle dynamometer. However, the concepts described herein can be applied in a similar manner to upper limb dynamometers, i.e., hand dynamometers. The invention can also be used in combinations of bicycles and hand dynamometers with two crank mechanisms. If the proposed technology is used in a hand dynamometer, the base bearing used is not, of course, a base bearing in the actual sense, but rather a crank bearing for such a hand dynamometer, and the pedal mechanism mentioned below is not a pedal mechanism in this case, but a rotational mechanism for the hand.

[0023] A key feature of the invention is that the bearings of the pedal device are mounted to be pivotable about a horizontal axis of rotation, wherein vibrations about this axis of rotation are preferably substantially only in one direction, preferably in the vertical direction.

[0024] Because of this installation, vibration can be selectively generated on the base bearing about the horizontal pivot, and the vibration acts only at that location.

[0025] According to a first preferred embodiment, the brake is preferably positioned at substantially the same horizontal height as the pedal assembly. The brake is coupled to the pedal assembly via a force-transmitting element, preferably in the form of a chain, timing belt, or V-belt. Furthermore, preferably, the bearings of the pedal assembly are mounted to be pivotable about a horizontal rotation axis, which is positioned at the same horizontal height as the brake shaft.

[0026] Typically, the rotation axis is preferably set horizontally.

[0027] The bearing base about the rotation axis can be provided by a generally fork-shaped structure, wherein the fork ends of the arms are mounted to be rotatable about the rotation axis, and the opposing converging arms are connected to the bearing, preferably, the converging region forming a bearing housing for the bearing of the pedal device.

[0028] Furthermore, preferably, the rotation axis can be configured such that pivoting motion at the bearing location is permitted primarily only in the vertical direction.

[0029] The vibration unit preferably has at least one main shaft, which is directly or indirectly driven by a motor, and the main shaft has an eccentric disk fixed thereon, wherein the eccentric disk is rotatably coupled to a connecting rod.

[0030] Furthermore, preferably, the connecting rod transmits vibration to the bearing of the pedal assembly via a connecting rod head, such that the vibration acts on the bearing substantially only in the vertical direction, with the connecting rod head positioned opposite one of the eccentric discs of the connecting rod. Combined with the bearing according to the invention, this vibration can be selectively applied to the base frame bearing.

[0031] Another preferred embodiment is characterized in that the vibration unit has at least one main shaft driven directly or indirectly by a motor, and the main shaft has an eccentric disk fastened thereto, wherein the eccentric disk is rotatably coupled to a connecting rod, the vibration unit is disposed below a bearing, and the connecting rod head is directly coupled to the bearing, preferably forming a bearing housing for the bearing, and the connecting rod alone, without any other guiding device, substantially supports the entire vertically downward load on the bearing.

[0032] Typically, the axis of the spindle is preferably set to be parallel to the axis of the bearing.

[0033] Another preferred embodiment is characterized in that the bearing of the pedal device is mounted in a vertical linear guide having a linear sliding portion, wherein the linear sliding portion is fixedly connected to the bearing at the top and connected to the connecting rod head at the bottom, wherein the axis of the main shaft is preferably parallel to the axis of the bearing.

[0034] In addition, a base plate can be provided, with the main shaft and motor preferably located below it and the pedal device located above it. A groove can be provided in the base plate, through which the connecting rod passes, and the connecting rod head is directly coupled to the bearing via the groove.

[0035] The vibration unit preferably has at least one main shaft, which is directly or indirectly driven by a motor, and the main shaft has an eccentric disk fastened thereto, wherein the eccentric disk is rotatably coupled to a connecting rod, and the vibration unit is disposed below the brake, preferably above the base plate, and wherein the coupling of the connecting rod to the bearing is preferably achieved by at least one support rod that extends obliquely upward and connects the connecting rod head directly or indirectly to the bearing, and wherein the support rod is also preferably rigidly connected to the base of the rotating shaft.

[0036] Another preferred embodiment is characterized in that the vibration unit has at least one main shaft driven directly or indirectly by a motor, and the main shaft has an eccentric disk fastened thereto, wherein the eccentric disk is rotatably coupled to a connecting rod, and another eccentric disk is disposed on the main shaft, through which a counterweight is disposed to compensate for vibration, wherein the other eccentric disk is preferably disposed on the main shaft with an eccentricity opposite to that of the eccentric disk used to drive the connecting rod.

[0037] Another eccentric disk preferably drives another connecting rod, which is rotatably mounted on the other eccentric disk and coupled to a counterweight, which is configured to vibrate substantially in the same direction as the vibrating device on the bearing, but has the function of compensating for the vibration on the bearing. Preferably, the vibration on the counterweight is offset by 180° relative to the vibration on the bearing.

[0038] Here, the brake is preferably positioned at substantially the same horizontal height as the pedal assembly, which brakes by means of a force-transmitting element, preferably in the form of a chain, timing belt, or V-belt, and coupled to the pedal assembly. The counterweight is mounted to be pivotable about a horizontal rotating shaft base, which is preferably positioned at the same horizontal height as the brake's shaft. The rotating shaft is preferably configured such that the counterweight in the bearing area performs pivoting motion substantially only in the vertical direction. The counterweight in the bearing area preferably has a counterweight head, which also preferably at least partially surrounds the top and bottom of the bearing area in a fork shape.

[0039] As an alternative to or supplement to this counterweighted compensation device, mounting the force gauge on a weighted plate can also prevent vibration of components that should not vibrate. This weighted plate typically has a weight of at least 50 kg, preferably greater than 100 kg, and can be, for example, a metal plate, sand container, water container, and / or stone element mounted on a platform within a height-adjustable frame. This frame can preferably be height-adjustable and / or leveled, optionally even electrically adjustable, and moved to the desired position via rollers (e.g., the rollers can be lowered simply for movement). The plate may also include damping elements; such damping elements are preferably located at the corners of the frame and / or the weighted plate, and / or damping pads can be provided for support on the frame or frame elements. Damping pads with a fine honeycomb elastic structure having a closed gas volume, such as damping pads based on polyether polyurethane with a thickness in the range of 10-30 mm, are particularly suitable. A mechanical high-pass filter can be provided, which largely prevents vibration of the device mounted on the floor, and also prevents vibration of components in the force gauge that should not vibrate. High-pass filters are particularly effective at filtering out vibrations below 25 Hz, preferably below 20 Hz.

[0040] The vibration unit may have at least one main shaft driven directly or indirectly by a motor, and the main shaft has an eccentric disk fastened thereto, wherein the eccentric disk is rotatably coupled to a connecting rod, and the eccentric disk and / or optionally another eccentric disk are mounted on the main shaft to be movable and adjustable in a direction perpendicular to the axis of rotation of the main shaft, wherein the mounting is preferably achieved by a door guide rail, wherein when at least one adjusting element moves along the axis of rotation of the main shaft, the eccentric disk moves in a direction perpendicular to the axis of rotation of the main shaft.

[0041] At least one adjusting element may be installed in a groove or through hole in the spindle so as to be adjustable by an actuation device, and the gate in or on the adjusting element may adjust the eccentricity of the eccentric disk by interacting with a slider on the eccentric disk.

[0042] The eccentric disk used to generate the desired vibration and another eccentric disk used for counterweight can be further mounted on the spindle. One or two separate adjustment elements can be provided. The eccentricity of the two eccentric disks can be adjusted in a related manner by the one adjustment element so that they are offset by 180°. The two separate adjustment elements can adjust the eccentricity of the corresponding disks respectively.

[0043] This type of force gauge is typically set to operate at a frequency of 1-50 Hz, with an amplitude at the bearing in the range of 1-10 mm, preferably in the range of 3-7 mm, and is preferably configured for loads in the range of 50-500 W, particularly in the range of 100-300 W.

[0044] The present invention also relates to the application of the above-mentioned force gauge in treatment and / or shaping therapy, wherein the frequency at the bearing is preferably adjusted in the range of 5-50Hz, preferably in the range of 7-25Hz, and / or the amplitude is adjusted in the range of 1-10mm, preferably in the range of 3-7mm.

[0045] The dependent claims will set forth further embodiments. Attached Figure Description

[0046] Preferred embodiments of the present invention will now be described with reference to the accompanying drawings, which are for illustrative purposes only and are not intended to be limiting. In the drawings:

[0047] Figure 1 An exploded view of the main components of the vibration unit for a force gauge according to a first embodiment is shown;

[0048] Figure 2 shows, in 2a), the following according to Figure 1 A cross-sectional view of the vibration element is shown in 2b). Figure 2a Details of A in );

[0049] Figure 3 An exploded view of the main components of the vibration unit of the force gauge according to the second embodiment is shown;

[0050] Figure 4 Showing according to Figure 3 Cross-sectional view of the vibration element;

[0051] Figure 5 An exploded view of the main components of the vibration unit of the force gauge according to the third embodiment is shown;

[0052] Figure 6 Showing according to Figure 5 Cross-sectional view of the vibration element;

[0053] Figure 7 shows different arrangements of the vibration unit, in which

[0054] 7a) shows an embodiment in which the base frame bearing is mounted directly from below via a rocker arm through a connecting rod;

[0055] 7b) shows an embodiment in which, without a swing arm, the base frame bearing is mounted in a linear mounting section, and the vibration unit is coupled to the linear mounting section from below;

[0056] 7c) shows an embodiment in which the vibration unit is disposed below the brake, the base frame bearing is mounted via a swing arm, and a counterweight is provided;

[0057] Figure 8 Showing according to Figure 7b A side view of an embodiment of );

[0058] Figure 9 shows the following based on Figure 7c ) is a view of an embodiment, wherein, for the sake of clarity of the individual components, 9a) shows the suspension without counterweight, and 9b) shows only the counterweight;

[0059] Figure 10 Different views are shown for another embodiment having a vibrating unit and a counterweight coupled to a swing arm, wherein a) is a right side view, b) is a left side view, c) is a top view, d) is an exploded view, e) is a top right view, and f) is a bottom right view. Detailed Implementation

[0060] Figure 1 The main components of the vibration unit are shown in an exploded view. The actual spindle 12 is mounted by two bearings 11 and rotated by a motor (not shown). Coupling can be direct or indirect, for example, via a V-belt. The motor is preferably a servo motor with an output in the range of 300-1600W. The spindle 12 here is structured and has an area on the left side 40 where the spindle 12 is mounted via the bearings 11. Two ball bearings 11 are used to mount the spindle 12 to the bearing housing 19 and prevent axial displacement of the spindle 12. A shoulder surface 12a is on the right side. This shoulder surface 12a prevents axial displacement of the eccentric disk 6 shown on the right side above, thereby preventing axial displacement of the entire connecting rod 1. The eccentric disk 6 is movably placed on the sliding surface 12b of the spindle. A sleeve 9 is held in the eccentric disk 6 in a form-fit manner and allows for eccentric adjustment of the eccentric disk 6 away from the axis of rotation of the spindle 12. The rotational force of the main shaft 12 is transmitted to the eccentric disk 6 via the sliding surface 12b and the housing 9, and then to the connecting rod 1. Here, the eccentric disk 6 is not directly supported on the sliding surface 12b of the main shaft, but the housing 9 is located between them. The housing 9 can be two parts, as shown in the figure, or it can be a single part. The contact surface 41 on the inner side of the eccentric disk 6 contacts the outer side of the housing 9 accordingly, and the contact surface 42 on the inner side of the housing 9 contacts the sliding surface 12b of the main shaft 12.

[0061] The housing 9 is preferably made of a material with frictional properties, such as a plastic material with frictional properties (e.g., PTFE), and the spindle 12 is made of metal in order to achieve optimal friction on the sliding surface 12b.

[0062] An eccentric disk 6 has a slider 5 in its axial groove 43. The slider 5 extends obliquely and laterally to the axis of the groove 43, determining the deflection of the eccentric disk 6 and thus the stroke of the connecting rod 1. The slider 5 spans the groove 43 and is secured by screws 7. The mounting screws 7 secure the slider 5 to the eccentric disk 6 not only by force but also by form. For mounting the connecting rod 1, a ball bearing is secured to the eccentric disk 6 by a bearing ring 3. Thus, the ball bearing via the bearing ring 3 is screwed onto the eccentric disk by screws 2. A clamping ring 8 is provided on the other side, which secures the outer ring of the ball bearing 4 to the connecting rod 1 by a screw 10 in a force-fit manner. The screw 10 clamps the ball bearing 4 onto the connecting rod 1 via the clamping ring 8.

[0063] The force of connecting rod 1 is transmitted to the main shaft 12 via eccentric disk 6 through sleeve 9, and to bearing housing 19 via bearing assembly 11. Connecting rod head 1a is used to house the bearing, which is used to movably fix to the linear unit or swing arm (see further below).

[0064] A studded adjusting element 13 is movably axially engaged in the axial blind bore 38 of the spindle 12. The adjusting element 13 is connected to the bearing housing 15 via a mounting screw 14 in a force-fit and form-fit manner. The bearing housing 15 houses a bearing assembly 16 in the form of two ball bearing rings. A trapezoidal threaded nut 17 mechanically connects (equivalent to preventing rotation) to the bearing housing 19 located on the bearing assembly 16. Figure 1 (Not shown in the image). Figure 1 The diagram also shows six holes for mounting screws onto the bearing housing 19. The bearing assembly 16 can be adjusted axially without clearance, and is secured by a shaft clamping nut 20 and a locking ring 21. Figure 1 (Not shown in Figure 2) It is fastened to the trapezoidal mandrel 18. The trapezoidal mandrel 18 moves the adjusting element 13 axially, thereby changing the stroke of the connecting rod 1. Due to the bearing assembly 16, the trapezoidal mandrel 18 does not rotate with the main shaft 12.

[0065] The adjusting element 13 is preferably made of a material with frictional properties, such as a plastic material with frictional properties (e.g., PTFE), and the slider 5 is made of metal in order to achieve optimal friction.

[0066] The door opening extends laterally within the adjusting element in the form of a cutout area 13a. This cutout area is substantially the same width as the thickness of the slider 5, but substantially longer. When the adjusting element 13 is pushed into the blind hole 38, the cutout area aligns with the larger opening 39. In other words, the slider 5 passes through both openings 39 and 13a. Therefore, the cutout area 13a is part of the adjusting element 13. The slider 5 is located within the cutout area 13a; the deflection of the eccentric disk 6 in a form-fitting manner is achieved through the plane of the slider 5 and the cutout area 13a of the adjusting element 13.

[0067] Therefore, the eccentric disk 6 is eccentrically mounted on the main shaft 12. The lower ring of the connecting rod 1 is rotatably mounted on the eccentric disk 6 via the bearing ring 4. When the main shaft 12 rotates, the eccentric disk 6 thus undergoes eccentric motion, which is transmitted to the lower ring of the connecting rod 1 and is converted into translation or oscillation at the connecting rod head 1a in this way. The oscillation frequency is determined by the rotational frequency of the main shaft 12, and therefore by the frequency of the motor driving the shaft. The amplitude of the oscillation can be adjusted by the trapezoidal mandrel 18. The adjusting element 13 is further pushed into the blind hole 31. The greater the distance the eccentric disk 6 moves out of the axis of the main shaft 12 via the slider 5, the greater the eccentric amplitude, and therefore the greater the amplitude of movement of the connecting rod head 1a. Therefore, the vibration generated at the connecting rod head 1a can be finely adjusted and controlled according to the frequency and amplitude. In addition, the connecting rod has high mechanical stability and very high directional stability, that is, the device proposed in this application allows quasi-unidirectional vibration with adjustable frequency and adjustable amplitude to be generated along a precisely defined direction.

[0068] Figure 2a The vibration element is roughly shown in cross-sectional view through the axis of the shaft, and Figure 2b ) shows Figure 2a Details of A in ) are shown. As can be seen, this type of vibration unit is positioned below the base plate 28, which serves as the central fastener for the vibration unit. The base plate has a groove 44 through which the connecting rod 1 protrudes freely upwards. On the underside of the base plate 28, one side is the left bearing housing 19 for mounting the main shaft, and the other side is the right bearing housing 19a for mounting the trapezoidal threaded nut 17.

[0069] The spindle 12 is mounted in the right bearing housing 19a via the aforementioned bearing 11. A shaft clamping nut 20 is provided for fastening purposes, which secures the bearing assembly 11 to minimize axial and radial clearance of the spindle 12. A locking ring 21 is also provided to prevent the shaft clamping nut 20 from accidentally loosening.

[0070] The bearing assembly 11 in Figure 2 is an O-ring bearing assembly. Force is engaged on the outside of the bearing assembly 11. Therefore, the radial and axial clearances of the spindle 12 are adjusted.

[0071] In this invention, the expected oscillation is only the deflection of the connecting rod head 1, which is substantially perpendicular to the base plate.

[0072] Figure 3A second exemplary embodiment of the vibration unit is shown in an exploded view, comprising two eccentric disks 6 mounted on the same shaft. In this case, two links 1 with shorter connecting arms are coupled to the two eccentric disks 6; one link is used to generate an effective vibration for the user, and the other link is used to generate the counterweight's reverse motion, as will be described below. The two eccentric disks 6 are disposed on the same main shaft 12, but each eccentric disk 6 has a separate sliding surface 12b relative to the main shaft 12, and the adjusting element 13 has two correspondingly designated cutout areas 13a with opposite tilt directions. However, in principle, the two eccentric disks 6 are mounted on the main shaft 12 and their eccentricity is controlled by the adjusting element 13 in a manner similar to that described in the first exemplary embodiment. Importantly, the eccentricity of the two eccentric disks 6 is configured to be phase-shifted by 180°, which is ensured by the reverse tilt of the cutout areas 13a and the corresponding reverse tilt of the two sliders 5 of the respective eccentric disk 6. If the adjusting element 13 is displaced in the groove 38 of the main shaft 12 by activating the trapezoidal mandrel 18, the trapezoidal mandrel 18 is secured by the locking ring 23 to prevent accidental loosening of the shaft clamping nut 22, which clamps the bearing assembly 16 in the bearing housing 15 to ensure axial and radial clearance-free installation of the trapezoidal threaded mandrel 18. One eccentric disc is quasi-offset in a first direction, while the other eccentric disc is quasi-offset in the opposite direction to the main shaft. This results in a 180° phase shift in the eccentricity of the two eccentric discs 6, specifically in a fully correlated manner, i.e., automatically adjusted by a single adjusting element 13 with opposite tilts of the notch area 13a to produce a precise 180° phase shift independent of the amplitude of the vibration adjustment. In this way, it is ensured that the optimal phase shift of the two links is always present, thus providing counterweight compensation in the best manner under any adjustment and any amplitude.

[0073] The second exemplary embodiment differs from the first exemplary embodiment, particularly in that the spindle 12 is coupled in a slightly different manner. Here, a V-belt pulley 24 is also provided for coupling the servo motor to the spindle via a V-belt. The V-belt pulley 24 is secured by a clamping nut, for example, in the form of a tapered locking bushing.

[0074] Therefore, the second embodiment differs from the first embodiment in that it can compensate for unexpected oscillations. Unexpected oscillations are understood to specifically refer to oscillations on the base plate 28 in the opposite direction to the expected oscillations, as well as other oscillations not perpendicular to the direction of the base plate 28. Unexpected oscillations are caused by unbalanced eccentricity, where the imbalance is mainly caused by the adjustability and structure of the connecting rod, which cannot achieve static equilibrium due to amplitude modulation of the stroke.

[0075] Figure 4A second exemplary embodiment is shown in a cross-sectional view. Referring to this figure, it can be seen in particular how the two connecting rods are mounted parallel to each other on the same spindle 12 via two eccentric discs, how the V-belt pulley 24 for coupling the servo motor protrudes on the left, and how the trapezoidal mandrel for adjusting the eccentricity protrudes on the right. Thus, a very compact solution in terms of structure is provided, in which two connecting rods absorbing high loads are mounted in a stable manner.

[0076] Figure 4 The bearing face of the connecting rod head bearing 26 is designed to be larger than that of the connecting rod head bearing 27 in order to absorb the forces that increase with load (e.g., under the influence of body weight) during operation.

[0077] Adjusting element 13 is used for corresponding sliders of the crank or for compensating the counterweight, extending in opposite directions. The two eccentric disks must be axially rotated 180° relative to each other to be able to deflect in opposite directions. This offset arrangement of the eccentric disks 6 can... Figure 1 It is better seen in the middle.

[0078] Figure 5 A third exemplary embodiment of the vibration unit is shown in the exploded view. Compared to the second exemplary embodiment, this third exemplary embodiment is configured such that the eccentricity of the two connecting rods 1 or the eccentricity of a designated eccentric disc can be adjusted separately for both. For this purpose, instead of installing 12 on one side of the main shaft and opening the other side for control via the adjusting element 13, bearing rings 11 are installed at both ends. See [reference needed] Figure 6 The cross-sectional view shows that the main shaft no longer has blind holes but instead has an axial through-hole, allowing individual adjusting elements 13 for adjusting the eccentricity of each eccentric disc 6 to be inserted from both sides. Therefore, there are trapezoidal mandrels 18 in both positions, each controlling a designated adjusting element 13. However, these two adjusting elements again have cutouts 13a with opposite inclination directions, allowing the eccentricity to be adjusted individually in principle, while still maintaining a 180° phase shift. This ensures the phase shift is always 180°, but the vibration amplitude can be set differently for the two links. In this way, the vibration compensation of the counterweight can be adjusted more finely, and especially adjusted according to environmental or user parameters to ensure optimal compensation.

[0079] Therefore, the third embodiment differs from the second embodiment in that the amplitudes of the two links can be controlled independently. According to this embodiment, unintended vibrations can be compensated for through oscillation balancing. Compared to the embodiment according to... Figure 3 and Figure 4The embodiment differs substantially in that the adjusting element 13 is configured in two parts. Both adjusting elements 13 require separate O-mounts and are actuated by a motor. The left trapezoidal spindle 18 controls the deflection of the compensation counterweight; the right trapezoidal spindle 18 controls the deflection of the crankshaft. In this embodiment, the drive of the main shaft 12 occurs at the center between the two connecting rods 1.

[0080] The compensation adjustment can be performed manually, but it can also be achieved by actuating one or more trapezoidal mandrels via another actuator. Therefore, such an actuator can be actuated via feedback control, for example, via one or more vibration sensors and a corresponding control unit. Thus, in particular, this control can also be performed in a self-learning algorithm, such that the vibration measured by the vibration sensor is minimized where vibration would not occur (e.g., on the base plate) and maximized or within the expected range where vibration would occur (e.g., on the base bearing).

[0081] Figure 6 It was an explosion. Figure 5 The cross-sectional view shows that the two adjusting elements 13 have different lengths. Figure 6 The linkage with zero stroke is shown. To change the stroke, the right adjusting element 13 moves to the right, and by rotating the trapezoidal spindle 18, the left adjusting element 13 also moves to the right; therefore, the deflection of the eccentric disk changes. Figure 6 In the middle, because the gap positions of the shell 9 are different (the right shell shows the gap at the top, and the left shell shows the gap at the bottom), the above-mentioned offset can be seen.

[0082] Figure 7 now shows the different possibilities for setting this type of vibration unit on a (bicycle) dynamometer.

[0083] Figure 7b and Figure 8 The side view shows the first possibility, in which the vibration unit is positioned below the base plate 28, such that the connecting rod 1 passes vertically upward through a groove in the base plate. Optionally, a base bearing 29 for mounting the force gauge is used to move in a strictly vertical direction in the linear sliding part 34, which is mounted on the base plate via a linear guide 35. This linear sliding part 34 is fixedly connected to the ball bearing 29 at the top and coupled to the connecting rod head 1a at the bottom.

[0084] The structure provided in this manner selectively achieves vibration only in a strictly vertical direction, and handles the entire suspension and load of the vibration unit through the front area below the base bearing. This vibration unit can be combined with a conventional brake 30 coupled to a force transmission element, such as a chain, belt, or timing belt.

[0085] In this structure, the vibration unit according to the first exemplary embodiment described above can be used, i.e., only one link is used for the vibration of the base frame bearing. However, the vibration unit according to the second or third exemplary embodiment can also be used. Figure 8 As shown, it is particularly possible that, via another link, the counterweight 36 is phase-shifted 180° within the housing, such that... Figure 8 The vibration of the first link shown above is transmitted to the base bearings at the desired frequency and amplitude, but vibrations related to the environment, particularly, for example, the base plate 28, are eliminated in a manner similar to noise cancellation. In reality, this type of equipment does present significant problems due to man-made vibrations. On the one hand, man-made vibrations lead to uncomfortable noise emissions, especially because the base plate or its corresponding legs transmit vibrations to the floor and building, etc.; however, uncomfortable noise emissions also exist due to vibrations from other components, such as, in particular, brakes. Furthermore, given the vibrations, this type of equipment tends to shift due to vibrations and moves almost everywhere. Last but not least, vibrations cause mechanical damage to the device itself and other components of the device, and also damage other nearby devices where the vibrations are unintentionally transmitted.

[0086] The type of vibration suitable for this device is typically in the range up to 50 Hz. Low frequencies of 7-12 Hz with an amplitude of 7-10 mm, used for nerve stimulation, typically with a load range of approximately 100 W, have proven particularly suitable. Higher frequencies in the 15-25 Hz range can be used for athletes, in which case they typically have a slightly lower amplitude of up to 3-4 mm. In this case, a load in the range of 200-300 W is used for braking output. Therefore, it is crucial that the vibration and amplitude are within the mechanically critical range for other components and that compensation by one or more counterweights is necessary.

[0087] Figure 7b The crank bearing is thus fixed to the linear bearing 35 via the sliding part 34, wherein the linear bearing 35 is arranged perpendicular to the base plate 28. The connecting rod is connected to the linear sliding part, thereby producing a movement that is completely perpendicular to the base plate 28. This structure can also be implemented in an oscillation-compensated manner by means of the counterweight 36 of the second slider on the second connecting rod and the linear guide.

[0088] Figure 7aThis illustrates another possibility for mounting such a vibration device on a force gauge. Similarly, the vibration is generated by link 1, extending substantially strictly in the vertical direction (see arrow). However, link 1 serves as the sole vertical mounting for the base bearing, thus providing an extremely slender structure. To make this structure possible, a swing arm 32 is also provided. This swing arm 32 is a second mounting for the base bearing, substantially surrounding the shaft 45 of the brake. The swing arm 32 has two arms 46, namely the first arm 46' and the second arm 46'. These two arms are joined at different ends of the shaft 45 and pivotally mounted on the base bearing 29. Since the shaft of the base bearing 29 and the shaft of the brake 45 are set at approximately the same horizontal height, it can be ensured that the swing arm 32 causes the base bearing 29 to move substantially only in the vertical direction at the base bearing seat, thereby ensuring strict vertical vibration. In such a force gauge, if the brake is set, for example, closer to the base plate or substantially lower than the base bearing, the swing arm 32 should not be mounted on the shaft of the brake, but rather on a separate axial bearing at approximately the horizontal height of the base bearing to precisely ensure that only vertical vibration occurs at the base bearing.

[0089] exist Figure 7a In this configuration, the center of the connecting rod head 1a coincides with the center of the crank bearing. The crank bearing is mounted solely on the connecting rod and rocker arm. Here, all forces except those in the connecting rod direction are absorbed by the rocker arm. The adjustable braking force of the brake 30 is transmitted to the crank 33 via the force transmission element 31. The braking effect can be adjusted using suitable methods known to those skilled in the art, such as translation between the crankshaft and the brake.

[0090] Figure 7c This illustrates another possibility for providing such a vibration device on a force gauge. The vibration device is positioned below the brake, with the base bearing quasi-free-floating. This results in a particularly compact and elegant construction. The swing arm 32 is again mounted to the brake shaft 45, and the base bearing 29 is mounted thereon, allowing the latter to move only in the vertical direction. In this configuration, the base bearing 29 is supported only in the vertical direction because the swing arm 32 has a strut that slopes downward toward the vibration device and is coupled to one of the two links of the vibration device via a connecting rod seat 37. In other words, the swing arm 32 includes a means for coupling the vibration of the vibration device, and the geometry and levers used ensure that the vibration at the base bearing is converted into a strictly vertical vibration, although the vibration at the device bearing on the connecting rod is in an inclined direction. See also Figure 9a The structure is shown in the figure, but for clarity, only the swing arm 32 with the strut 46 is shown.

[0091] Figure 7cTherefore, a variation is shown in which the oscillation drive is not located below the ball bearing, but rather outside the crank region. Thus, the components below the crankshaft are eliminated, enabling a very compact structural design. The connecting rod is movably connected to the rocker arm at the connecting rod seat 37 of the rocker arm.

[0092] In this configuration, the corresponding counterweight 36 is advantageously mounted in a very similar manner and driven by a second link with a 180° phase shift. See especially... Figure 9b This diagram illustrates the structure of the counterweight, omitting the swing arm for the base bearing. In this case, the counterweight 36, or more precisely, the counterweight head 50, is mounted to the brake shaft 45 via a first support rod 47 in a manner similar to a swing arm. On the other side, between the counterweight head 50 and the connecting rod seat 37a for the counterweight, there is a support rod 49 pointing downwards, and a third support rod 48 that mounts the counterweight connecting rod seat to the brake shaft 45 to ensure the stability required for the installation. Thus, the counterweight, especially its counterweight head 50, is installed in the most space-saving manner, while still protruding between the two arms 46' and 46" of the swing arm, and also provides optimal compensation.

[0093] Figure 10 Another exemplary embodiment of the force gauge is shown. Components identical to their counterparts described above have the same reference numerals. In this exemplary embodiment, the swing arm is designed with multiple struts on both sides, and in particular, additional vertical and horizontal struts. However, in principle, the attachment to the connecting rod 1 is similar to the attachments described in Figures 7 and 9 above. The counterweight is also mounted in a similar manner; here, the counterweight head 50 is constructed as a layered body, and by adding more layers, the mass of the counterweight head can be adapted to any site. Furthermore, the weight head 50 is configured as a fork, meaning that the fork arms at least partially surround the base bearing 29 at the top and bottom. In this way, the counterweight can be ideally positioned close to and within the base bearing area, thereby enabling optimal vibration compensation. Here, the counterweight is mounted via a mounting body 47, which is also configured with multiple struts, and is further coupled to the vibration unit via a connecting rod seat 37a for the counterweight. This mounting body penetrates the struts of the swing arm in some sense, thus achieving optimal, space-saving, and compact mounting.

[0094] In this exemplary embodiment, it can also be seen that the actuator 52 has a designated V-belt 51 for adjusting the trapezoidal threaded nut, and correspondingly for adjusting the eccentricity and the associated vibration amplitude. A motor 54 for driving the spindle 12 and a corresponding V-belt 53 can also be seen.

[0095] List of reference numerals

[0096] 1 link

[0097] 1' Linkage for counterweight

[0098] 1a connecting rod head

[0099] 2 screws

[0100] 3 bearing rings

[0101] 4 ball bearings

[0102] 5 sliders

[0103] 6 eccentric discs

[0104] 6' Eccentric disc for counterweight

[0105] 7 mounting screws

[0106] 8 clamping rings

[0107] 9 shells

[0108] 10 screws

[0109] 11 Bearing Assembly

[0110] 12 spindles

[0111] 12a Shoulder surface

[0112] 12b Sliding surface

[0113] 13 Adjustment elements

[0114] 13a incision area

[0115] 14 mounting screws

[0116] 15 bearing housing

[0117] 16 bearing assembly

[0118] 17 Trapezoidal Thread Nut

[0119] 18 trapezoidal mandrels

[0120] 19 Left Bearing Housing

[0121] 19a Right Bearing Housing

[0122] 20-axis clamping nut

[0123] 21 lock rings

[0124] 22-axis clamping nut

[0125] 23 lock rings

[0126] 24V type pulley

[0127] 25 clamping nut

[0128] 26 connecting rod head bearing

[0129] 27 connecting rod head bearing

[0130] 28 base plate

[0131] 29 Crank Bearing

[0132] 30 brakes

[0133] 31 Force Transmission Components

[0134] 32 swing arm

[0135] 33 crank

[0136] 34 linear sliding section

[0137] 35 Linear Guide Section

[0138] 36 counterweights

[0139] 37-link swing arm

[0140] 37a connecting rod seat counterweight

[0141] Axial blind hole in 38 12

[0142] 39 radial through holes

[0143] 40 12 fastening area

[0144] 41 6 on the contact surface of 9

[0145] 42 9 on the contact surface of 12b

[0146] The groove in 43 6

[0147] The groove for 1 in 44 28

[0148] 45 Brake Shaft

[0149] 46 32 support rod

[0150] 46', 46" 32 arms

[0151] 47 Counterweight support rod to the brake shaft

[0152] 48. Counterweight support rod from the brake shaft to the counterweight connecting rod seat.

[0153] 49 From the counterweight connecting rod seat to the counterweight head counterweight support rod

[0154] 50 counterweight head

[0155] 51 V-band for starting trapezoidal threaded nuts

[0156] 52 is used to start the motor of the trapezoidal threaded nut via 51.

[0157] 53 V-belt for the drive motor of spindle 12

[0158] 54 Motors used to drive spindle 12

Claims

1. A force gauge, comprising a bicycle force gauge, having at least one pedal mechanism for a user, and having a vibration unit, in, The bearing (29) of the pedal device is mounted so as to be pivotable about a horizontal rotation axis (45); The vibration unit has at least one main shaft (12), which is directly or indirectly driven by a motor (54), and the main shaft (12) has an eccentric disk (6) fixed thereon, wherein the eccentric disk (6) is rotatably coupled to a connecting rod (1), and The connecting rod (1) transmits vibration to the bearing (29) of the pedal device through the connecting rod head (1a), such that the vibration acts on the bearing (29) only in the vertical direction, and the connecting rod head (1a) is configured to be opposite to one of the eccentric discs (6) of the connecting rod (1).

2. The force gauge according to claim 1, characterized in that, The brake (30) is positioned at the same horizontal level as the pedal assembly, wherein the brake (30) is coupled to the pedal assembly via a force transmission element (31), and wherein the bearing (29) of the pedal assembly is mounted to be pivotable about the horizontal rotation axis (45) at the horizontal level of the shaft (45) of the brake (30).

3. The force gauge according to claim 2, characterized in that, The force transmission element (31) is in the form of a chain, a timing belt, or a V-belt.

4. The force gauge according to claim 1, characterized in that, The rotating shaft base of the bearing (29) is defined by a fork-shaped structure.

5. The force gauge according to claim 1, characterized in that, The rotating shaft base of the bearing (29) is defined by a fork-shaped structure, the fork ends of the arms (46', 46") are mounted to be rotatable about the rotating shaft, and the arms converge relative to the bearing (29), the convergent region forming the bearing seat of the bearing (29) for the pedal device.

6. The force gauge according to claim 1, characterized in that, The rotating shaft (45) is configured such that the pivoting motion of the bearing (29) is only permitted in the vertical direction.

7. The force gauge according to claim 1, characterized in that, The vibration unit has at least one main shaft (12), which is directly or indirectly driven by a motor (54), and the main shaft (12) has an eccentric disk (6) fixed thereon, wherein the eccentric disk (6) is rotatably connected to a connecting rod (1), and The vibration unit is positioned below the bearing (29), and the connecting rod head (1a) is directly coupled to the bearing (29). The connecting rod (1) alone, without any other guiding device, supports the entire vertically downward load on the bearing (29). Alternatively, the bearing (29) of the pedal device is mounted in a vertical guide (35) having a linear sliding portion (34), wherein the linear sliding portion (34) is fixedly connected to the bearing (29) at the top and to the connecting rod head (1a) at the bottom.

8. The force gauge according to claim 1, characterized in that, The vibration unit is disposed below the bearing (29), and the connecting rod head (1a) is directly coupled to the bearing (29) and forms the bearing housing of the bearing (29). The connecting rod (1) alone, without any other guiding device, supports the entire vertically downward load on the bearing (29), wherein the axis of the main shaft (12) is parallel to the axis of the bearing (29). Or characterized in The bearing (29) of the pedal device is mounted in a vertical guide (35) having a linear sliding part (34), wherein the linear sliding part (34) is fixedly connected to the bearing (29) at the top and connected to the connecting rod head (1a) at the bottom, wherein the axis of the main shaft (12) is parallel to the axis of the bearing (29).

9. The force gauge according to claim 7, characterized in that, A base plate (28) is provided, the main shaft (12) is located below it, and the pedal device is located above it. A base plate groove (44) is provided in the base plate (28), the connecting rod (1) passes through the base plate groove (44), and the connecting rod head (1a) is directly coupled to the bearing (29) through the base plate groove (44).

10. The force gauge according to claim 7, characterized in that, A base plate (28) is provided, the main shaft (12) and the motor are located below it, and the pedal device is located above it. A base plate groove (44) is provided in the base plate (28), the connecting rod (1) passes through the base plate groove (44), and the connecting rod head (1a) is directly coupled to the bearing (29) through the base plate groove (44).

11. The force gauge according to claim 2, characterized in that, The vibration unit has at least one main shaft (12) driven directly or indirectly by a motor (54), and the main shaft (12) has an eccentric disk (6) fixed thereon, wherein the eccentric disk (6) is rotatably coupled to the connecting rod (1), and the vibration unit is disposed below the brake (30).

12. The force gauge according to claim 2, characterized in that, The vibration unit has at least one main shaft (12) driven directly or indirectly by a motor (54), and the main shaft (12) has an eccentric disk (6) fixed thereon, wherein the eccentric disk (6) is rotatably coupled to a connecting rod (1), and the vibration unit is located below the brake (30) and above the base plate (28), wherein the coupling between the connecting rod (1) and the bearing (29) is achieved by at least one support rod (46), the support rod (46) extending obliquely upward and connecting the connecting rod head (1a) directly or indirectly to the bearing (29), and wherein the support rod (46) is further rigidly connected to the rotating shaft base of the bearing (29).

13. The force gauge according to claim 1, characterized in that, The force gauge is mounted on a base plate, which serves as a mechanical high-pass filter for vibrations generated by the vibration unit and / or the base plate, and / or the vibration unit has at least one main shaft (12) driven directly or indirectly by a motor (54), and the main shaft (12) has an eccentric disk (6) fixed thereon, wherein the eccentric disk (6) is rotatably coupled to a connecting rod (1), and another eccentric disk (6') is disposed on the main shaft (12), through which a counterweight (36) is provided in the compensation vibration.

14. The force gauge according to claim 1, characterized in that, Another eccentric disk (6') is disposed on the main shaft (12), and a counterweight (36) is disposed on the other eccentric disk (6') to compensate for vibration. The other eccentric disk (6') is disposed on the main shaft with an eccentricity opposite to that of the eccentric disk (6) to drive the connecting rod. The other eccentric disk (6') drives another connecting rod (1'), which is rotatably mounted on the other eccentric disk (6') and coupled to the counterweight (36). The counterweight (36) is configured to vibrate in the same direction as the vibration unit on the bearing (29) and has the function of compensating for the vibration on the bearing (29). The vibration of the counterweight (36) is offset by 180° relative to the vibration of the bearing (29).

15. The force gauge according to claim 13, characterized in that, The brake (30) is positioned at the same horizontal level as the pedal assembly, wherein the brake (30) is coupled to the pedal assembly via a force transmission element (31), and the counterweight (36) is mounted to be pivotable about a horizontal axis of rotation.

16. The force gauge according to claim 15, characterized in that, The counterweight (36) is mounted to be pivotable about a horizontal rotating shaft base, which is positioned at the same level as the shaft (45) of the brake (30), wherein the rotating shaft (45) is configured such that the counterweight (36) in the bearing (29) region pivots only in the vertical direction, wherein the counterweight (36) in the bearing (29) region has a counterweight head (50), and the counterweight head (50) at least partially surrounds the top and bottom bearing regions in a fork shape.

17. The force gauge according to claim 1, characterized in that, The vibration unit has at least one main shaft (12) driven directly or indirectly by a motor (54), and the main shaft (12) has an eccentric disk (6) fixed thereon, wherein the eccentric disk (6) is rotatably coupled to a connecting rod (1), and the eccentric disk (6) and / or an optional other eccentric disk (6') are mounted on the main shaft (12) to be movable and adjustable in a direction perpendicular to the axis of rotation of the main shaft (12).

18. The force gauge according to claim 17, characterized in that, The installation is achieved by a door guide (5, 13a), wherein when moving along the axis of the main shaft (12), at least one adjusting element (13) causes the eccentric disk (6) to be displaced along the axis of rotation perpendicular to the main shaft.

19. The force gauge according to claim 18, characterized in that, At least one of the adjustment elements (13) is installed in the adjustment element groove (38) or through hole of the main shaft (12) to be adjustablely moved by the actuation device (18), and the door (13a) in or on the adjustment element adjusts the eccentricity of the eccentric disk (6) by interacting with the slider (5) on the eccentric disk (6).

20. The force gauge according to claim 18, characterized in that, An eccentric disk (6) for generating the desired vibration and another eccentric disk (6') for counterweight are mounted on the main shaft (12), and the eccentricity of the two eccentric disks is adjusted in a related manner by setting one of the adjustment elements (13) to offset them by 180°, or two separate adjustment elements are set to adjust the eccentricity of the corresponding eccentric disk (6) and the other eccentric disk (6') respectively.

21. The force gauge according to claim 1, characterized in that, The force gauge is used to operate at a frequency of 1-50 Hz, with the vibration amplitude at the bearing (29) in the range of 1-10 mm, or the load in the range of 50-500 W.

22. The force gauge according to claim 21, characterized in that, The vibration amplitude at the bearing (29) is in the range of 3-7 mm.

23. The force gauge according to claim 21, characterized in that, The load range is 100-300W.

Images